Air conditioner



H. A. WHITESEL AIR CONDITIONER May 16, 1961 4 Sheets-Sheet 1 Filed Nov. 12, 1958 INVENTOR. HARRY A, WI- ITESEL A T TOE/YE Y y 1961 H. A. WHlTESEL 7 2,984,089

AIR CONDITIONER Filed Nov. 12, 1958 4 Sheets-Sheet 2 IN V EN TOR.

fig HARRY A. WH/TESEL ATTORNE Y y 15, 1961 H. A. WHITESEL 2,984,089

AIR CONDITIONER Filed Nov. 12, 1958 4 Sheets-Sheet 3 2 Ann JNVENTOR. Haze) H. VVH/TESEL Law y 16, 1961 H. A. WHITESEL 2,984,089

' AIR CONDITIONER Filed Nov. 12, 1958 4 Sheets-Sheet 4 INVENTOR. Z7 HAERY A. will TESEL im? @MW AQTTOENEY United States Patent "i 2,9s4,0s9 AIR CONDITIONER Harry A. 'Whitesel, Cedar Rapids, Iowa, assignor to Amana Refrigeration, Inc., Amana, Iowa, a corporation of Iowa Filed Nov. 12, 1958, Ser. No. 773,473

19 Claims. (Cl. 62-429) The present invention pertains to air conditioners, particularly air conditioners adapted to be mounted in a wall or window of a room and air circulating and refrigerant cooling means therefor.

Present window air conditioners, especially those of larger capacity, are heavy, bulky and often quite noisy. If their inner face is kept more or less flush with the window casement, the unit, owing to its large depth, protrudes in a very unsightly manner outside the window, and a special shelf and brackets are needed for support. Many of the larger conditioners are too wide to fit between the sides of many windows which limits the cooling capacity of a unit suitable for such windows. Furthermore, present-day window units tend to be quite high and thus greatly decrease the amount of light admitted through a window in which they are installed.

The air conditioner of the present invention permits the size, noise and weight of a unit of given capacity to be greatly reduced, particularly in depth, as compared with the usual unit of the same capacity. This reduction has been accomplished both by greatly increased elflciency and by compact design. For instance, a window air conditioner of the present invention having a one ton ca pacity measures 25 inches wide, 13% inches high and 16% inches deep, compared with approximately 25, 15 and 28 inches, respectively, for a typicalunit of the same capacity now available. Obviously, therefore, an air conditioner of the present invention can easily be mounted upon the sill of many windows without even the need of any brackets to support its exterior andyet have its inner face closely flush with the inner casement of the window. Its minimum height allows a maximum amount of light to be. transmitted by the window. Likewise, if the unit is permanently mounted through an opening in a wall of the room, as is often done nowadays, it will protrude inside and outside very little and sometimes not at all, depending, of course, upon the thickness of the wall.

The compactness, efficiency and silence of the air conditioner of the present invention is achieved in part by a novel arrangement of the evaporator and condenser fans. Two centrifugal-type fans, surrounded by air scrolls, the condenser fan and scroll being of the double inlet type, are used and mounted on opposite'sides of a partition between the room air and outside air passages. The condenser scroll has its inlets within a chamber into which outside air is drawn through the condenser by the condenser fan. One motor drives both fans and is also mounted upon the partition with substantially its entire housing encompassed within a portion of the condenser fan. Most any kind of fan employing the centrifugal principle will do so long as at least one of its inlets is of suflicientsize to receive the bulk of the fan motor therein. Cage type blowers are used in the embodiment hereinafter described because they are economical and give excellent results with a minimum height. If the latter dimension is not tooimportant, other kinds I frigerators, freezers and so forth.

of centrifugal fans may be used with an even "greater reduction in depth of the unit, but with an increase in height, for a given cooling capacity. Whatever form of centrifugal fan is used, the resulting depth of the entire blower assembly is thus little more than the sum of the widths of the condenser and evaporator scrolls. The fan unit, as it is mounted wholly on a single partition, is readily removed as a unit from the air conditioner for service and to permit better access to other parts of the remaining mechanism.

The use of a double inlet blower and scroll for the condenser permits one of the blower inlets to be placed much-closer to the condenser coil than would be possible were a propeller-type of fan to be used, inasmuch as the other inlet causes air to be drawn through that portion of the coil not directly opposite the first blower inlet. In the arrangement of the present invention about 70% of the incoming air through the condenser is drawn in by the scroll inlet close to the condenser while the remaining 30% is drawn through the edges of the condenser by the other scroll inlet. Propeller-type fans, even if a shroud is used, must be some distance from the face of the coil, especially if a small diameter fan is used, in order that there be air flow through the entire coil. Furthermore, centrifugal blowers are quieter and work more efficiently than propeller-type fans against high static pressures, which in turn allows the use of a much closer finned and thus much smaller coil, as well as lower fan speeds, for a given capacity. Similarly, a centrifugal blower for the evaporator allows the use of a much smaller evaporator coil for a given capacity. Accordingly, all dimensions of the present air conditioning unit, particularly the height and the depth, are very greatly reduced by the present blower arrangement. The blower arrangement itself is in turn also adaptable in part or in whole to other refrigerating uses where a compact and eflicient blower system is required.

' The efliciency of the air conditioner of the present invention is further increased by the provision of a desuperheater coil adjacent the condenser coil, and by arranging these two coils with regard to the condenser blower so that the maximum cooling efliciency is obtained from the air flow produced by the latter. Indeed, the combination of these two coils with the condenser blower of the present invention provides a highly compact and eflicient refrigerant cooling unit suitable for incorporation in any air cooled refrigerating system, such as re- In the present arrangement the hot refrigerant from the motor-compressor unit is led first entirely through the de-superheater, which is of such size as to remove just the superheat from the refrigerant. Then the refrigerant is passed through the condenser to remove the latent heat. The relatively cool outside air, is pulled in through the condenser by the condenser blower and blown out by the latter through the de-superheater. Since the coil capacity needed to remove the superheat is less than that needed to remove the latent heat, the de-superheater coil can be smaller and use less rows than the condenser coil, which in turn promotes the air flow through the latter. Furthermore, both coils are proportioned so that the total resistance of each to the air flow is substantially equal and thus, for well-known reasons, the maximum possible airflow for a given blower system is obtainedthrough both coils. A water slinger is provided on the end of the condenser blower which sprays condensate drained from the evaporator on to the condenser,

is superior in several respects to the usual single condenser found in prior window air conditioners. In the latter, for instance, a porton of the coil removes the superheat and the remaining portion the latent heat. Accordingly, part of the cool outside air is used only to remove the superheat, yet there is sufiicient cooling capacity in the outside air to remove both the superheat and the latent heat. Thus, to use a part of the outside air to remove the superheat alone, wastes a portion of its cooling capacity. Therefore, for a given coil capacity, more air, by the use of a larger fan or higher fan speed, is required to remove the latent heat, which in turn means increased size and noise of the unit.

In the arrangement of the present invention, on the other hand, all of the relatively cool outside air is first used to remove the latent heat from the refrigerant, and the same air, though warmed by its removal of the latent heat, is still sufficiently cool ascompared with the refrigerant in the de-superheater, to remove the superheat therefrom. In the single condenser type of unit, a similar result is sometimes attempted by proportioning the coil and routing the hot refrigerant so that the last row downstream of the air flow removes the superheat and the remaining upstream rows the latent heat. However, such an arrangement increases the thickness of the coil necessary and thus the size of the entire air conditioning unit. Also, it prevents the most eflicient use of the condensate to cool the condenser bymeans of a slinger ring. Even more important, it is impossible to make the air flow resistance of each of the two portions of the coil equal in order to have maximum air flow through 'both. If, instead, the condenser extends over the full area of the rear of the unit, in order that the coil be as thin as possible, then louvres must be provided in the sides or top or bottom to admit or discharge'the condenser cooling air, depending upon the latters direction through the condenser, but such louvres are more or less prohibited if the unit is to be thin enough to be encompassed within a wall or window casing, unless special ducts are used.

Furthermore a single condenser, no matter what its size, does not operate at a constant temperature throughout the path of the refrigerant therethrough, in contrast to the condenser in the present invention which removes only the latent heat from the refrigerant. This is because in single-stage condenser units there is a certain amount of leak-back of heat through the connecting fins from the superheat portion to the latent heat portion. In the present air conditioner the de-superheater is entirely separate from the condenser so that there is no conduction from the former to the latter.

Accordingly, it is the principal object of the present invention 'to provide an air conditioner of minimum overall dimensions and high efliciency for a given cooling capacity.

Another object of the present invention is the provision of a compact but eflicient air cooled refrigerant condensing system.

A further object of the present invention is the provision of an air conditioner having a high efficiency twostage refrigerant condensing unit, employing a de-superheater.

Another object of the present invention is the provision of compact, silent and efficient air circulation means for a refrigerant evaporator and condenser system.

A further object of the present invention is to provide an air conditioner whose air circulating means are easily 'removeable as a unit for servicing.

Other and further objects, features and advantages will be apparent from the description of the preferred form of the invention which follows, read in connection with the accompanying drawings inwhic'h:

Figure 1 is an exploded,'perspective view of the front of the air conditioner with the cover removed and with certain portions cut away;

Figure 2 is a perspective view of the rear of the air conditioner with various portions cut away;

Figure 3 is a plan view of the air conditioner with the cover removed;

Figure 4 is an exploded, perspective front view of the air conditioner base and partition assembly on the one hand and the refrigerant coils and their connections on the other hand; and

Figure 5 is an exploded, perspective rear view of the air conditioner base and partition assembly showing the blower system removed as a unit.

In order to facilitate understanding of the invention, reference is made to the embodiments thereof shown in the accompanying drawings and detailed descriptive language is employed. It will, nevertheless, be understood that no limitation of the invention is thereby intended and that various changes and alterations are contemplated such as would ordinarily occur to one skilled in the art to which the invention relates.

Referring now to the drawings, the enclosing and supporting structure of the air conditioner comprises a case or housing composed of cover 10 provided with any form of suitable air permeable grills 11 and 12 for the room face or front and the outside face or back thereof, respectively, and a rectangular base pan 13. Cover 10 fits down over base pan 13 and is removably secured in any suitable fashion to upturned flange 14 around the periphery of the latter.

Mounted upon base pan 13 are vertical partitions 15, 16, 17 and 18. Partition 15 is parallel to the ends of base pan 13 and approximately in the middle thereof. Partition 17 is parallel to partition 15 and inset slightly from one end of base pan 13 to form with cover 10 a fresh air passage 19 extending from back to front of the unit. Partition 16 has its ends removably secured to partitions 15 and 17 and is at right angles thereto. Partitions 15, 16 and 17 form with base pan 13 and cover 10 a room air intake chamber 20 and an outside air intake chamber 21 each having an outlet therefrom cominunicating with the room air and the outside air respectively, through portions of grills 11 and 12. Partition 18 is angled from approximately the middle of partition -15 to the other side of base pan 13 near the front edge thereof to form with partition 15, base pan 13 and cover 10 a room air outlet chamber 22 and a larger outside air outlet chamber 23 each having an outlet therefrom communicating with the room air and the outside air respectively, through the remaining portions of grills 11 and 12. The outer vertical edge of partition 18 is provided with an angular gasket seat 24 and the top edges of partitions 15, 16, 17, and 18 and the front vertical edge of partition 15 are bent to 'forrnflanges 25 adapted to abut cover 10. In seat 24 and upon the horizontal portions of flange 25 which with cover 10 form chamber 22, gaskets 26 are secured in order to sell ofi chamber 22 from chambers 20, 21 and 23 when cover 10 is installed. To prevent excessive collection of rain water or condensate on base pan 13, overflow drain holes 27 are provided in the rear portion of flange 14 of base pan 13 and in the corresponding locations in cover 10. Partitions 15, 16 and 17 may also be provided with scuppers along the bottom edges in order to'distribute rain Water or condensate equally upon the respective portions of base pan 13.

The refrigerating system, which is charged with a suitable refrigerant, comprises evaporator 30 of the usual multi-row type of finned coil but with relatively closely spaced -fins. The bottom of evaporator 30 is spaced from base pan 13 and evaporator 30 itself is secured in an upright position parallel to grill 11 between its end plates 31 and 31', the latter being attached in turn to the front vertical edges of partitions 15 and 18, respectively. Evaporator 30 thus extends across the room air outlet from chamber 22. Beneath evaporator 30 andcovering the flo'or of chamber 22is secured an insulating block 3 2 ofany suitable plastic material having formed therein condensatecollector basin 33 and drain trough34 leadingfrorn the latter through partition 15 to the floor of chamber 21. The-insulating properties of block 32 pre vent evaporator from causing any sweating of the floor of chamberf22 and thus any water dripping therefrom into the room.., De-superheater 35, which is usually a single r'ow, closely finned coil, stands upright parallel. to grill 12 between its end plates 36 and 36 with the.

bottom edge of plate 36 attached to the back portion of flange 14 by clip 37 whichengages one of drain holes 27. The lower end ofplate 36' is in turn secured to the back portion of flange 14 by screw 38 or similar means.

Condenser 39, usually a ,multi-row coil with closelyv base pan 13 does .not seep between block 32 and the floor of chamber 22. I,

Motor compressor 41, which is of the usual hermetically sealed type, is mounted on base pan 13 in chamber 23 by means of vibration damping mountings 42. The hot refrigerant is led from theoutput or high side of motor compressor 41 through line 43 to the input at the bottom of de-superheater 35. The output of the latter isconnected in turn by line 44, which also holds de superheater 35 in an upright position, to the input at the top of condenser 39. The liquid refrigerant from the outlet at the bottom of condenser 39 is led through return line 45 out of which it is taken in the usual manner by capillary 46 to input '47 at the top of evaporator 30'. The output of the latter feeds into collector 48 and through suction line 49 to the input or suction side of motor compressor 41, thus completing the refrigerant circuit. Capillary 46 is soldered to the underside of suction line 49 in order to chill the liquid, refrigerant from condenser 39 still further. If desired, *a subcooler may also be provided by first leading return line 45: from condenser 39 through the condensate collected on the floor of chamber 21.

. It will be appreciated, of course, that the sizes and number of rows of evaporator 30, de-superheater 35 and condenser 39 and the size and length of capillary 46 depend upon the cooling capacity of a particular unit and the refrigerant-employed. However, de-superheater 35 and condenser 39 are so proportioned capacity-wise, as between themselves, so. that for the particular cooling rating of the unit, the characteristics of the refrigerant used and the available air flowqthrough each coil, desuperheater 35 is sufiicient to remove the superheat and condenser 39 the latent heat from the hot refrigerant. In addition; de-superheater 35 and condenser 39 are also proportionedso that the resistance of each to air flow therethrough issubstantially the same.

These proportions are readily accomplished by a proper relation between the face area, the number of fins and the thickness of each coil. .Since less capacity isneeded to remove the superheat than to remove the latent heat from the refrigerant, condenser 39 may have two or more rows of coils and de-superheater 35 perhaps but one row. Thus, the face area of each can be proportioned so that the resistance of each to airflow therethrou-gh is very closely equal; for instance, the face area of condenser 39 may be twice that of de-superheater 35. The spacing of the tins of each coil, however,is kept as close aspossible in order that the overall size of each coil beas small,as possible. The foregoing calculations and those for the remaining-elementsofthe refrigerating system can be readily-madeby one skilled in the artto which the invention r'elatesr r The blower assembly is entirely mounted upon partition,

16 andcomprises cylindricalblower motor 50 of standard type, one end of which is secured to the middle of partition 116 so that its shaft is horizontal and its housing projects into chamber 21. Theshaft of motor 50 is double-ended and one end 51 thereof passes through partition 16 into chamber 20 and its other end 52 extends close to the inner face of condenser 39. Room air,

scroll 53 is secured to chamber 20 side of partition 16, the latter forming one end of scroll 53 and a vertical end partition 54 extending between partitions 15 and 17 and parallel to partition 16 forming the other end. Scroll 53 is provided with a single, circular air inlet 55 through partition 54 and is surrounded by inlet ring 56 in axial alignment with the shaft end 51 of motor 50. -An' air outlet 57 from scroll 53 is provided through partition 15 to chamber 22. Chamber 20, scroll 53 and chamber 22 thus form a passage or duct for the room air. able single inlet blower 58 of the centrifugal type within scroll 53 with its inlet facing inlet 55 is driven from shaft end 51, the inner diameters of blower 58 and inlet ring 56 being such as to provide for a smooth flow of room housing of motor50 as possible intrudes within scroll-59.: The diameter of the aforesaid cutout is of suflicient size so as to form with the motor housing an annular inlet 63 to scroll 59, and end 60 of the latter is spaced from parti tion 16 just enough to provide a suflicient access to inlet 63 for air from chamber 21. The depths of chamber 21 and scroll 59 aresuch that the other end 61 of the latter is thereby positioned close to the inner face of condenser 39. End 61 is provided with a circular air inlet 64 therein surrounded by inlet ring 65 in axial alignment with the shaft end 52 of motor 50. Scroll 59 is further provided with an outlet 67 therefrom through partition 16 into chamber 23. Chamber 21, scroll 59 and chamber 23 thus form a passage or duct for the outside -A suitable double inlet blower 66 of the centrifugal type within scroll 59 with its respective inlets opposite inlets 63 and 64 is driven from shaft end 52, the diameters of blower 66, inlet ring 565 and annular inlet 63 being such as to provide for a smooth flow of outside air from chamber 21 to within blower 66. The edges of partition 54; and the edges of outlets57 Zand67 from scrolls 53 and 59, respectively, are provided with flanges-'68 which are not.

secured to but merely abut their respective portions of partitions 15 and 17. There is thus provided a compact blower assembly which is removably secured as a unit to partitions 15 and 17.

A circular water slinger. 69 ofconventional design is positioned between the inner face of condenser 39 and the face of inlet 64 and also driven from shaft end 52. Slinger 69-is of such diameter that its periphery comes to within about A inch of base pan 13. The necessaryspeed and size of blowers 58 and 66 and motor 50 and the size of scrolls 53 and 59 for a unit of given cooling capacity are readily determined by one skilled in the to which the invention pertains.-.

The front vertical edge ofpartition 17 is provided with" a rectangular fresh air inlet 70 from fresh air passage 19. An air filter 71 of any suitable kind is removably posi-' tioned between partitions 15 and 17 on the one hand, and. parallel to partition 54 between the latterand fresh'airv inlet 70 on the other hand. To prevent contactbetween filter 71 and any condensate. on the floorof, chamber 20,. the bottom edge of filter'71 rests upon a stand 72'moun'ted j on base pan 13.- -A fresh air damper 73, operable-by crank-74, is hinged to partition. 17 so that inits'operr A suit- End 60 of position a portion of the adjacent, vertical, edge of filter is across the inner or frontend of passage 19 (see Figure 3). I

Any of a number of well-known controls, as indicated generally at 75, may be provided for motor compressor 41, motor 50 and damper 71, and if desired a humidity responsive control, reverse cycle connectionsand control, or a. room airexhaust arrangement may also be readily adapted to the unit. The controls themselves may be in: dependently operated as shown, or may be dependently connected to a master control of the kind shown, for example, in United States Patent No. 2,811,022 to Lathrop. Suitable. cool air directing vanes may be, provided for the airoutlet portion of grill '11 and adjusted by a control such as indicated at 76.

The path of the refrigerant and the operation of desuperheater 35 and condenser 39 thereupon have already been described. When the unit is placed in a window or awall of a room and motor compressor 41 and blower motor 50 are in operation, rotation of blower 66 causes inlet 64 to draw outside air through that portion of condenser 39 directly opposite thereto and annular inlet 63 to draw outside air into the entire chamber 21 through the remaining portions of condenser 39. The provision of annular inlet 63 thus permits inlet 64 to be as close as possible to the inner face of condenser 39 and yet insures that air will be drawn through the entire surface of condenser 39 (see Figure 3). The air entering blower 66 cools motor 50, is then expelled through outlet 67, around motor compressor 41, thus contributing also to its cooling, and finally is returned to the outside through desuperheater 35 and its portion of grill 12. Since de-superheater 35 is proportioned to remove the superheat from the refrigerant, its temperature is higher than that of condenser 39 proportioned to remove the latent heat. Thus the air passing through the former is still cool enough to reduce the temperature of the refrigerant therein, even though that air has been warmed by its passage through the lattter.

Condensate from evaporator 30 drains into basin 33 and from there down trough 34 on to the floor of compartment 21. When the condensate level rises above /16 inch, it is picked up by slinger 69 and thrown against the incoming air stream onto condenser 39, further increasing the cooling capacity of the latter. Any condensate not evaporated on condenser 39 is returned to the floor of chamber 21 or is carried in the air stream through scroll 59 and on to de-superheater 35, augmenting its cooling capacity. Proportioningde-superheater 35- and condenser 39 to have substantially equal resistance to the air flow therethrough results in maximum possible air flow through each for a given pumping capacity of blower 66'. Consequently, de sup'erheater 35 and condenser 39, together with motor-50, scroll S9 and blower 66 provide a compact but highly efficient refrigerant condensing system.

. Room air to be cooled is drawn through grill 11, through filter 71 and into blower 58 through inlet 55. The fact that motor 50 is within blower 66 instead of blower 58 or otherwise in chamber 20, prevents rnotor heat from being communicated to the room air. Blower 58 expels the air from outlet 57 and returns it to the room through evaporator 30 and grill 11. If a mixture of fresh air is desired, damper 73 may be opened whereby outside air will also be drawn into bl'ower 58 through the edge of filter'71 from passage 19 leading to'the outside air through grill 12 (see Figure 3). t

Inasmuch as the entire blower assembly is mounted on partition 16', removal of its fastenings to partitions 15" and 17 afterremoval of case'10permits the entire assembly readilyto be withdrawn as a unit for servicing and cleaning and to allow better access to the remainder of thejair conditioner,

If a more.economicalconstructionof the airconditi'oneris desired, de superheate r 35' may be eliminated and condenser 39 extended across the entire rear oftheunit' so that a part of the condenser will be cooled by the incoming outside air to inlets 63 and 64 andv the. remainder by the same air upon its return to the outside through chamber 23-. However, the advantages of a de-superair flow therethrough is to be suflicient.

Having now described my inventon, what I claim is new and desire to secure by Letters Patent is: V t

1. An air conditioner foran enclosed space comprising a'refrigerating system including an evaporator and a condenser, a condenser air passage having an inlet and outlet-to the ouside air and an evaporator air passage having an inlet and outlet to the inside air, air circulating means operatively associated with each of said passages to move air therethrough, said condenser and evaporator being positioned in heat exchange relationwith the cir culating air in their respective passages, a de-superheater positioned in heat exchange relation with the circulating air in said condenser passage and downstream of said condenser, whereby outside air moved through said con denser air passage by said air circulating means is first passed in heat exchange relation with said condenser and then in heat exchange relation'withsaid de-superheater, said de-superheater being connected intosaid refrigerating system so that all of the refrigerant passes through said de-superheater before passing through said condenser, 35

and the heat exchange capacity of said de-superheater and said condenser being so proportioned between each other relative to the temperature and quantity both of the refrigerant flowing therethrough and the air passing in heat exchange therewith that the superheat of the refrigerant is removed by the former and the latent heat by the latter.

2. A room air conditioner comprising a housing, a refrigerating system within said housing includingan evaporator and a condenser, a condenser air passage within said housing having an inlet and outlet to the outside air and an evaporator air passage within said housing having an inlet and outlet tothe inside air, said passages having a common partition therebe tween forming at least a portion of each of said passages and said condenser and evaporator being mounted in heat exchange relation with the air in their respective passages, said condenser being adapted to achieve said heat exchange relation by air fiow therethrough, air circulating means within said housing for each of said passages, said means for said condenser air passage including a condenser air scroll therein having an outlet therein dividing said passage into a portion downstream of said outlet and a portion upstream thereof, said scroll having opposite first and second air inlets in said upstream portion with said first inlet adjacent and spaced from one side of said partition, said second inlet being adjacent and spaced from the downstream face of said condenser, a centrifugal blower having an air inlet at each of its axial ends and axially disposed within said scroll between said blower inlets in air circulating relation with said inlets and outlet of said scroll, a blower motor mounted on said side of said partition and adapted to have. asubstantial portion thereof intrude from said side into said blower through portions of said first inlet of said scroll and the corresponding axial inlet of said blower, one end of the shaft of said motor'driving said blower, a de-superheater'positioned in heat exchange'relation with the air in said condenser passage and downstream of said air scroll outlet, whereby outside air moved through said condenser air'passag'e is-first passed in heat exchange relation with saidcondensen and then: in heat. exchange relation with said de-superheater;.saidl dersuper heater being connected into said refrigerating system so thatall of the refrigerant passes through said de-superheaterbefore passing through said condenser, the heat exchange capacity of said de-superheater and said condenser being so proportioned between each other relative to the temperature and quantity both of the refrigerant and air passing therethrough in heat exchange relation that the superheat of the refrigerant is removed by the former and the latent heat by the latter and being so phy-. sically proportioned that the air pressure drop caused by each upon the air flowing through said condenser passage in heat exchange relation with each is substantially equal. 3. The device of claim 2 wherein said air circulation means for said evaporator air passage includes an evaporator air scroll adjacent the other side of said partition, said evaporator scroll having an outlet therein dividing said evaporator passage into a portion downstream of said outlet, and a portion upstream thereof, said scroll having an air inlet in said upstream portion, a centrifugal blower: having an air inlet thereto and disposed within said scroll in air circulating relation with said inlet and outlet of said scroll, said blower being driven from the other end of said motor shaft. :4. A compact, room air conditioner comprising a room air circulating chamber having a room air inlet and outlet therein, an outside air circulating chamber divided into upstream and downstream portions having respectively an outside air inlet and outlet therein, a common partition between said room air chamber and said upstream portion of said outside chamber, at least a portion of said partition being opposite and facing the air inlet in said upstream portion, air circulating means for said outside air chamber, said means comprising an air scroll having opposite ends within said upstream portion, oneof said ends being adjacent and closely spaced from one side of said partition and the other facing said inlet in said upstream portion, an air inlet in each of said ends, an air outlet from said scroll opening into said downstream portion, a centrifugal blower having an air inlet in each of its axial ends and axially disposed within said scroll between said ends thereof, each of said blower inlets facing one of said scroll inlets in air circulating relation with the inlets and outlet of said scroll, a blower motor mounted on said side of said partition and adapted to have a substantial portion thereof project therefrom to within said blower through portions of the inlets in said adjacent end of said scroll and the corresponding axial 'end of said blower, one end of the shaft of said motor driving said blower, a refrigerant condenser of the finned coil type positioned at the inlet to said upstream portion in 'heatexchange relation with the air flowing therethrough and having a downstream face adjacent and closely spaced from the inlet in said non-adjacent end of said scroll, the air path from said face to'said non-adjacent inlet being substantially unobstructed except by said scroll, air circulating means for moving air through said room .air chamber, a refrigerant evaporator positioned in heat exchange relation with, room air moved through said room air chamber, a refrigerant de-superheater of the finned coil type p ositioned at the outlet from said upstream portion in' heat exchange relation with the air moving therethrough, a motordriven refrigerant compressor in one of said-chambers, said condenser, evaporator, de-superheater and ct impressor being operatively connected in refrigerating relation and charged with refrigerant so that all of the refrigerant passes through said de-superheater before passing through said condenser, the heat exchange capacity of said de-superheater being proportioned between each other'relative to the temperature and quantity both of the refrigerant and the air flowing therethrough in heat exchange relation to remove the superheat and said condenser the latent heat from the refrigerant and being, each physically proportioned to offer substantially equal n 5. The device of claim 1 wheren said condenser and dc superheater are so physically proportioned that the air pressure drop caused by each upon the air flowing through said condenser passage in heat exchange relation with each is substantially equal.

6. The device of claim 1 wherein said air circulating means for said condenser air passage comprises an air scroll therein having an air outlet and oppositely facing first and second air inlets in air flow relation with said condenser air passage, said first scroll inlet being spaced from an inner wall of said passage downstream of said condenser, a motor driven centrifugal fan with said scroll in air pumping relation to each of said scroll inlets and said scroll outlet, and wherein said condenser is adapted to achieve said heat exchange relation by air flow therethrough and has a downstream face spaced closely from said second scroll inlet.

7. An air cooled refrigerant condensing system comprising an air circulating passage having an air inlet and outlet, a refrigerant condenser positioned in heat exchange relation with air circulated through said passage and having its output adapted for connection to a refrigerant evaporator, air circulating means operatively associated with said passage to move air therethrough, a de-super-- heater positioned in heat exchange relation with air circulated in said passage and downstream of said condenser and having its input adapted for connection to a refrigerant compressor and its output connected to said condenser so that all of the refrigerant passes first through said de-superheater and then through said condenser, the heat exchange capacity of said de-superheater and said condenser being so proportioned between each other relative to the temperature and quantity both of the refrigerant flowing therethrough and the air passing in heat exchange therewith that the superheat of the refrigerant is removed by the former and the latent heat by the latter.

8. The device of claim 7 wherein said condenser and de-superheater are so physically proportioned that the air pressure drop caused by each upon the air flow through said condenser passage in heat exchange relation with each is substantially equal.

9. A compact, air cooled refrigerant condensing system comprising an air circulating passage having an air inlet and outlet, a refrigerant condenser positioned in heat exchange relation With air circulated through said passage and having its output adapted for connection to a refrigerant evaporator, said condenser being adapted to achieve said heat exchanger relation by air flow there-j through, motor-driven air circulating means operatively associated with said passage to move air therethrough, said means including an air scroll having a pair of oppositely facing first andsecond air inlets from and an air outlet to said passage, said first inlet being adjacent and closely spaced from the downstream face of said condenser and said second inlet being adjacent and closelyspaced from an inner wall of said passage downstream of said condenser, a de-superheater positioned in heat ex change relation with air circulated in said passage and downstream of said condenser and having its input adapted for connection to a refrigerant compressor and its out-' put connectedv to said condenser so that all of the refrigerant passes first through said desuperheater and then through said condenser, the heat exchange capacity of said de-superheater and said condenser being so proportioned between each other relative to the temperature and quantity both of the refrigerant flowing therethrough and the air passing in heat exchange therewith that the superheat of the refrigerant is removed by the former and the latent heat byhe latter.

10. The device of claim 9 wherein said motor-driven air, circulating means includes acentrifugal fan having an air inlet in each of its axial ends and axially disposed within said scroll, between said inlets thereof and a motor for said fan mounted on said inner wall and adapted to have a substantial portion thereof protrude from said wall into said scroll through portions of said second scroll inlet and the corresponding axial inlet of said fan.

11. An air conditioner for an enclosed space comprising a refrigeration system including refrigerant evaporating and refrigerant condensing means, an air passage for said condensing means having an inlet and outlet to the outside air and an air passage for said evaporating means having an inlet and outlet to the inside air, said condensing and evaporating means being positioned in heat exchange relation with the air in their respective passages, said refrigerant means for one of said passages being adapted to achieve said heat exchange relation by airflow therethrough, air circulating means operatively associated with each of said passages to move air therethrough, said circulating means for said one of said passages including an air scroll having first and second air inlets downstream of said refrigerant means for said passage and an air outlet in air flow relation with said passage and said refrigerant means, said first inlet being adjacent and spaced from an inner wall of said passage and said second inlet being spaced from the downstream face of said refrigerant means, a centrifugal fan within said scroll in air pumping relation to each of said scroll inlets and said scroll outlet, de-superheating means positioned in heat exchange relation with the circulating air in said passage for said condensing means and downstream thereof, said de-superheating means being connected into said refrigerating system so that all of the refrigerant passes through said de-superheating means before passing through said condensing means, and the heat exchange capacity of said de-superheating means and said condensing means being so proportioned between each other relative to the temperature and quantity both of the refrigerant flowing therethrough and the air passing in heat exchange therewith that the superheat is removed by the former and the latent heat by the latter.

12. A compact air conditioner for an enclosed space comprising a pair of air circulating passages for circulation of outside air through one and inside air through the other, a refrigerating system including refrigerant condensing means in heat exchange relation with the air in said outside air passage and refrigerant evaporating means in heat exchange relation with the air in said inside air passage, said refrigerant means for one of said passages being adapted to achieve said heat exchange relation by air flow therethrough and having a downstream face, air circulating means operatively associated with each of said passages to move air therethrough, said circulating means for said one of said passages including a centrifugal fan and a fan scroll operatively positioned thereabout having an air outlet to and a pair of air inlets from said passage downstream of said face, the mouth of one of said inlets being closely spaced from and substantially parallel to said face and the other inlet being adjacent and closely spaced from an inner wall of said passage, the air path from said face to said other inlet being arranged to promote air flow therebetween.

13. In a compact, self-contained room cooler having a pair of air circulating ducts for circulation of outside air through one and room air through the other, a refrigerating system including a condenser in heat exchange relation with the air in said outside air duct and an evaporator in heat exchange relation with the air in said room air duct, said condenser being adapted to achieve said heat exchange relation by air flow therethrough and having a downstream face, the combination therewith of air circulating means for each of said ducts, said means for said condenser duct including an air scroll having an air outlet and first and second air inlets downstream of said face in air flow relation with said duct and a centrifugal fan disposed within said scroll in air pumping relationwith' said outletiand each of said inlets, the.

mouth of said first inlet being adjacent and closely spaced s 12 from a wall of said duct and the mouth of said second inlet being substantially parallel to and closely spaced from said face, the air path from said face to said first inlet being arranged to promote air flow therebetween.

14. In a compact, self-contained room cooler having a pair of air circulating ducts for circulation of outside air through one and room air through the other, a refrigerating system including a condenser in heat ex-' change relation with the air in said outside air duct and an evaporator in heat exchange relation with the air in said room air duct, said condenser being adapted to achieve said heat exchange relation by air flow therethrough and having a downstream face, the combination therewith of air circulating means for each of said ducts, said means for said condenser duct including an air scroll having an air outlet and opposite first and second air inlets downstream of said face in air flow relation with said duct and a centrifugal fan having opposite axially located inlets disposed within said scroll in air pumping relation with said outlet and each of said inlets thereof, the mouth of said first inlet being adjacent and closely spaced from a wall of said duct and the mouth of said second inlet being substantially parallel to and closely spaced from said fact, the air path from said face to said first inlet being arranged to promote air flow therebetween, and a motor for rotating said fan mounted so that its body is wholly within said condenser duct with a substantially portion thereof projecting within said fan through portions of said first inlet and the corresponding axial inlet of said fan.

15. In a compact air conditioner for an enclosed space having a pair of compartments for circulation of outside air through one and room air through the other, said outside air compartment having a pair of opposite parallel walls, a refrigerating system including a condenser of the finned coil type in heat exchange with the air in said outside air compartment with its downstream face forming forming one of said walls and an evaporator in heat exchange relation with the air in said room air compartment, the combination therewith of air circulating means for each of said compartments, said means for said condenser compartment including an air scroll therein having an air outlet and opposite first and second air inlets downstream of said face, a motor driven centrifugal fan having opposite axially located inlets disposed within said scroll in air pumping relation between said inlets, the mouth of said first inlet being closely spaced from and substantially parallel to the other of said walls and the mouth of said second inlet being closely spaced from and substantially parallel to said face, the air path from said face to said first inlet being arranged to promote air flow therebetween.

16. In a compact air conditioner for an enclosed space having a pair of compartments for circulation of outside air through one and room air through the other, said outside air compartment having a pair of opposite parallel walls, a refrigerating system including a condenser of the finned coil type in heat exchange with the air in said outside air compartment with its downstream face forming one of said walls and an evaporator in heat exchange relation with the air in said room air compartment, the combination therewith of air circulating means for each of said compartments, said means for said condenser compartment including an air scroll therein having an air outlet and opposite first and second airinlets downstream of said face, a motor-driven centrifugal fan having opposite axially located inlets and disposed within said scroll in air pumping relation between said inlets, the mouth of said first inlet being closely spaced from and substantially parallel to the other of said walls and the mouth of said second inlet being closely spaced from and substantially parallel to said face, the air path fromsaid face to said ,first inlet being arranged to promote air 13 compartment, a substantial portion of said body projecting within said fan through portions of said first inlet and the corresponding axial inlet of said fan, one end of the motor shaft driving said fan.

17. The device of claim 16 wherein said air circulating means for said room air compartment comprises a second air scroll positioned adjacent the other side of said other wall opposite said first scroll, said second scroll having an air inlet in said room air compartment and an air outlet therefrom, and a second centrifugal fan disposed within said second scroll in air circulating relation with said outlet and inlet thereof, said second fan being driven from the other end of said motor shaft.

18. A compact, air cooled refrigerant condensing system comprising an air circulating passage having an air inlet and outlet, a refrigerant condenser positioned in heat exchange relation with air circulated through said passage and having its input adapted for connection to a refrigerant compressor and its output adapted for connection to a refrigerant evaporator, said condenser being adapted to achieve said heat exchange relation by air flow therethrough and having a downstream face, an air scroll forming a portion of said passage having first and second air inlets therein in air flow relation with the portion of said passage upstream of said scroll and downstream of said face and an air outlet therein in air flow relation with the portion of said passage downstream of said scroll, a motor-driven centrifugal fan within said scroll in air circulating relation with said inlets and outlet thereof, the mouth of said first inlet being closely spaced from an inner wall of said passage and the mouth of said second inlet being closely spaced from and substantially parallel to said face, the air path from said face to said first inlet being arranged to promote air flow therebetween,

19. A compact, air cooled refrigerant condensing system comprising an air circulating passage having an air inlet and outlet, a refrigerant condenser positioned in heat exchange relation with air circulated through said passage and having its input adapted for connection to a refrigerant compressor and its output adapted for connection to a refrigerant evaporator, said condenser being adapted to achieve said heat exchange relation by airflow therethrough and having a downstream face forming a wall of said passage, an air scroll forming a portion of said passage having opposite first and second air inlets therein in air flow relation with the portion of said passage upstream of said scroll and downstream of said face and an air outlet therein in air flow relation with the portion of said passage downstream of said scroll, a motor-driven centrifugal fan having opposite axially located inlets disposed within said scroll in air circulating relation between said inlets, the mount of said first inlet being closely spaced from a wall of said passage opposite to and downstream of said face and said second inlet being closely spaced from and substantially parallel to said face, the air path from said face to said first inlet being arranged to promote airflow therebetween, and a fan motor mounted with its body wholly within said passage with a substantial portion thereof projecting within said fan through portions of said first scroll inlet and the corresponding axial inlet of said fan, the shaft of said motor driving said fan.

References Cited in the file of this patent UNITED STATES PATENTS 2,329,342 Ditzler Sept. 14, 1943 2,386,883 Ames Oct. 16, 1945 2,719,410 Deering Oct. 4, 1955 2,751,760 Williams June 26, 1956 2,823,852 Busch Feb. 18, 1958 2,945,362 Gould July 19, 1960 

